EP1649193B1 - Tensionneur reglable - Google Patents

Tensionneur reglable Download PDF

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Publication number
EP1649193B1
EP1649193B1 EP04776900A EP04776900A EP1649193B1 EP 1649193 B1 EP1649193 B1 EP 1649193B1 EP 04776900 A EP04776900 A EP 04776900A EP 04776900 A EP04776900 A EP 04776900A EP 1649193 B1 EP1649193 B1 EP 1649193B1
Authority
EP
European Patent Office
Prior art keywords
pivot
arm
shoe
base
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04776900A
Other languages
German (de)
English (en)
Other versions
EP1649193A1 (fr
Inventor
Andrzej Dec
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gates Corp
Original Assignee
Gates Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gates Corp filed Critical Gates Corp
Priority to PL04776900T priority Critical patent/PL1649193T3/pl
Publication of EP1649193A1 publication Critical patent/EP1649193A1/fr
Application granted granted Critical
Publication of EP1649193B1 publication Critical patent/EP1649193B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0846—Means for varying tension of belts, ropes, or chains comprising a mechanical stopper

Definitions

  • the invention relates to a tensioner, more particularly, to a tensioner having an adjustable base, according to the preamble of claim 1.
  • Belt tensioners designed for synchronous drives cannot accommodate the movement necessary to properly remove slack from belt drives having long length belts.
  • the primary object of the invention is to provide a tensioner having an adjustment feature for setting a base position with respect to an indicated predetermined belt spring force.
  • an adjustable tensioner comprising:
  • Fig. 1 is a front view schematic of a synchronous (timing) belt drive system of the automotive type which includes a tensioner of the invention.
  • Fig. 2 is a sectional view taken along the line of 2-2 of Fig. 3 and showing an enlarged tensioner of the invention.
  • Fig. 3 is a sectional view taken along the line 3-3 of Fig. 2 .
  • Fig. 4 is a perspective view showing an interrelationship of certain features of the invention.
  • Fig. 5 is a plan view of the tensioner showing the adjustment feature.
  • Fig. 6 is a plan view of the tensioner showing the adjustment feature.
  • a synchronous or "timing" belt drive system 10 includes a toothed belt 12 entrained and tensioned around a crank pulley 14, an idler pulley 16, and a water pump pulley 18, cam shaft pulleys 20, 21 and a tensioning pulley 22 of a tensioner 24 of the invention.
  • the tensioning pulley 22 engages the belt 12 and receives a belt load in the form of belt tension of adjacent belt spans 26, 28.
  • the belt tension of the spans generate a belt force component BF which is referred to as the "hub load.”
  • the belt force component BF occurs along a bisector of an angle formed between the belt spans 26, 28.
  • the tensioner includes a base 30 and a pivot-arm 32 that oscillates about a pivot 34.
  • Pivot 34 may be in the form of a fastener used to secure the tensioner to an engine (not shown).
  • Pulley 22 is journaled to the pivot-arm and engages belt 12 and receiving the belt force BF.
  • Compression spring 36 has a first end 38 operatively connected to the pivot-arm 32 such as by a boss 40 located at an operative radius 42 in relation to the pivot.
  • a damping mechanism 43 is also included.
  • Bushings 44, 44' are interpositioned between the pivot and pivot-arm in known fashion.
  • the pulley is attached to the pivot-arm by way of a ball bearing 45, also in known fashion.
  • Base 30 further comprises a tool receiving portion 92 which is described in Figs. 5-6 .
  • the pivot-arm 32 includes an extension 46 or portion in the form of a concave arcuate surface 47 that moves with the pivot-arm and is spaced a radial distance 48 from the pivot 34.
  • the concave arcuate surface 47 is oriented to generally face the pivot 34 and a second end 50 of the compression spring 36.
  • Arcuate surface 47 being substantially concentric with the pivot and optionally, has a radial distance 48 that is equal to or greater than the operative radius 42 for greater damping. Put another way, the larger the radius 48, the larger a resultant damping torque for a given damping force.
  • Damping mechanism 43 includes a moveable shoe 52 with a convex arcuate friction surface 54 that is complimentary to and engages concave arcuate surface 47 of pivot-arm portion 46.
  • the shoe may be in two-part form with a pad of friction material engaged with surface 47 and attached to and backed up by the shoe.
  • Shoe 52 has a ramp surface 56, and a spring receiving portion such as a boss 58. The spring receiving portion faces and attaches the second end 50 of the compression spring.
  • the ramp surface 56 engages a protuberance 60 which is secured to or part of the base.
  • Protuberance 60 has a complimentary ramp surface 62 that engages the ramp surface 56 of the shoe.
  • the ramp surface of the protuberance is oriented at a divergent angle R in relation to a longitudinal axis 64 of the spring.
  • the compression spring 36 being biased between the pivot-arm and shoe, operates to press the convex surface 54 of the shoe against the concave surface 47 of the pivot-arm 32 to effect damping.
  • the damping coefficient is a function of the spring rate of the spring 36. The greater the spring rate the greater the damping coefficient.
  • the forces on the shoe 52 are balanced in such a manner to keep the shoe pressed against the ramp surface 62 when the arcuate surface oscillates in movement between a clockwise direction A and counterclockwise direction B.
  • the ramp surface also operates to hold the second end of the spring in a substantially fixed position relative to the base by way of the boss 58.
  • Compression spring 36 exerts a spring force SF on the shoe pressing the convex arcuate surface 54 against the concave arcuate surface 47 wedging the ramp surface 56 of the shoe against the ramp surface 62 of the protuberance 60.
  • the concave surface 47 exerts a reactionary force CF against the shoe and the ramp surface 62 exerts a reactionary force RF against the shoe.
  • the summation of these forces operate to position the shoe against the ramp surface 62 which is secured to or formed of the base by way of the protuberance 60.
  • tensioner 24 is located adjacent its installed position to an automotive engine.
  • Fasteners such as the pivot bolt 34 and another pin or bolt 66, attach and locate the tensioner in a fixed position on an engine (not shown).
  • Toothed belt 12 is then entrained around the crank pulley 14, idler pulley 16, water pump pulley 18, and cam pulleys 20, 21.
  • a wrenching surface 68 is provided as a means to rotate the tensioner with a wrench (in this case counterclockwise B) to a position away from the belt for easy belt installation. With the belt in the correct position, the pivot-arm is rotated (clockwise A) to where the pulley presses the belt to its belt engaging position as shown in FIG. 1 .
  • Toothed belt 12 is tensioned as the pulley is positioned in pressing engagement against the belt.
  • the base 30, which may be in the form of a second pivot-arm that moves around the pivot 34, is then held in a fixed position relative to the engine by the fasteners 34, 66.
  • Figs. 5-6 describe the adjustment feature for adjusting a spring force.
  • the pulley is pressed into engagement with the belt by means of the compression spring pushing on the pivot-arm at its operative radius 42 so as to rotate the pivot-arm which in this case is clockwise A.
  • the compression spring also presses against the moveable shoe 52 which is held in position relative to the base 30 by means of the engaged ramp surfaces 56, 62.
  • Spring 36 presses the convex arcuate surface 54 of the shoe against the concave arcuate surface 47 of the pivot-arm.
  • the concave arcuate surface 47 angularly oscillates A-B in response to angular movements of the pivot-arm 32.
  • the shoe 52 operates to damp angular movements of the pivot-arm by friction surface sliding between the concave arcuate surface 47 of the pivot-arm and convex arcuate surface 54 of the shoe.
  • the balance of forces from engaged ramp surfaces 56, 62, engaged arcuate surface, and spring operate to keep the second end 50 of the spring in substantially a fixed position in relation to the base 30 so that the spring can operate to bias the pivot-arm and press the pulley against the belt.
  • the belt will press against the pulley with an increased force BF that operates to rotate the pivot-arm counterclockwise B and further compress the compression spring 36 resulting in an increased spring force SF.
  • the increase in spring force operates to press against the damping shoe with increased force against the shoe and thereby increases friction surface sliding between the concave and convex arcuate surface 47, 54 which operate to inhibit the pivot-arm from moving in the counterclockwise direction B.
  • Fig. 5 is a plan view of the tensioner showing the adjustment feature.
  • the adjustment feature shown in Figs. 5-6 allows the tensioner to be installed to a predetermined spring force SF.
  • tool receiving portion 92 radially extends from base 30 with respect to pivot 34.
  • Tool receiving portion comprises a hole 93 for receiving a known tool (T), such as a 3/8" or 1 ⁇ 2" ratchet for example.
  • T a known tool
  • the tool receiving portion 92 radially extends beyond the damping mechanism 43 with respect to the pivot rendering portion 92 easily accessible for use.
  • Base 30 includes an indicator portion 91.
  • Pivot arm 32 has an indicating portion 90 disposed to cooperate with indicator portion 91 to indicate a relative state of spring load.
  • Fig. 5 shows the tensioner with spring 36 (not shown) in a fully extended or decompressed position. Protuberance 60 is engaged with pivot-arm 32 by action of spring 36. One can see that indicator portion 91 and indicator portion 90 are not aligned in this pre-installation configuration.
  • Fig. 6 is a plan view of the tensioner showing the adjustment feature.
  • tensioner 24 is located adjacent its installed position to an automotive engine and fasteners such as the pivot bolt 34 and another pin or bolt 66, attach and locate the tensioner in a fixed position on an engine (not shown).
  • the toothed belt 12 is entrained around the crank pulley 14, idler pulley 16, water pump pulley 18, and cam pulleys 20, 21 as shown in Fig. 1 .
  • Pivot 34 and bolt 66 are loosely engaged with a mounting surface, but are not fully torqued.
  • a tool (T) is inserted into portion 92. With the belt in the correct position as described, the base 30 and pivot arm are rotated (clockwise A) until the pulley presses the belt to its belt engaging position as shown in FIG. 1 . Slot 96 allows oscillation of pivot arm 32 about bolt 66. Using tool (T) base 30 is then rotated further about pivot 34 until indicator 91 aligns with notch 90. Slot 95 allows base 30 to rotate about pivot 34. Rotation of base 30 with respect to pivot arm 32 about pivot 34 compresses spring 36. An alignment of 90 and 91 indicate a proper spring force SF and hence belt tension has been achieved. The spring load or force SF is a function of the spring rate for spring 36 and the amount of spring compression necessary to align 90 and 91.
  • the spring rate for spring 36 can be selected as required to accommodate a desired operating condition.
  • Pivot 34 and bolt 66 are torqued into place.
  • Pivot arm 32 pivots about pivot 34 during operation.
  • Bolt 66 in conjunction with pivot 34 immovably attaches base 30 to the mounting surface.
  • Tool (T) is then removed.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Vibration Prevention Devices (AREA)
  • Springs (AREA)
  • Vibration Dampers (AREA)
  • Vehicle Body Suspensions (AREA)
  • Body Structure For Vehicles (AREA)
  • Load-Engaging Elements For Cranes (AREA)

Claims (5)

  1. Tendeur réglable comprenant :
    une base (30) ;
    un bras de pivotement (32) qui oscille autour d'un pivot (34) fixé à la base (30) ;
    une poulie (22) fixée au bras de pivotement (32) et destinée à engager une courroie (12) ;
    un ressort de compression (36) pourvu d'une première extrémité (38) fonctionnellement reliée au bras de pivotement (32) au niveau d'un rayon opérant par rapport au pivot (34) ;
    et un mécanisme d'amortissement (43) qui empêche les mouvements oscillatoires du bras de pivotement (32) ;
    le bras de pivotement (32) comprenant une surface arquée concave (47) qui se déplace avec le bras de pivotement (32) et est espacée d'une distance du pivot (34), la surface arquée concave (47) étant orientée pour être généralement tournée vers le pivot (34) et une deuxième extrémité (50) du ressort de compression (36) ;
    le mécanisme d'amortissement comprenant un patin (52) mobile ayant une surface de friction arquée convexe (54) complémentaire de, et venant en prise avec, la surface arquée concave (47) du bras de pivotement (32), une partie de réception de ressort qui est tournée vers, et se fixe à, la deuxième extrémité (50) du ressort de compression (36), et une partie de surface (56) qui vient en prise avec une protubérance (60) fixée à la base (30), le ressort (36) appliquant une force élastique contre le patin (52) pressant la surface arquée convexe (54) contre la surface concave (47) produisant une force de réaction sur le patin (52), la force élastique et la force de réaction se combinant pour presser le patin (52) contre la protubérance (60), l'amélioration consistant en ce que le tendeur est caractérisé par :
    une partie de réglage s'étendant depuis la base comprenant une partie de réception d'outil (92) ;
    une partie indicatrice (90) sur le bras de pivotement (32) ;
    une partie indicatrice (91) disposée sur la base (30) pour coopérer avec la partie indicatrice (90) sur le bras de pivotement (32) afin d'indiquer une force de ressort de compression prédéterminée.
  2. Tendeur selon la revendication 1, dans lequel la partie de surface (56) du patin d'amortissement (52) et la protubérance (60) se présentent sous la forme de surfaces inclinées complémentaires, orientées dans la direction d'un angle divergent par rapport à un axe longitudinal du ressort de compression.
  3. Tendeur selon la revendication 1, dans lequel la surface arquée concave (47) du bras de pivotement (32) est sensiblement concentrique au pivot (34).
  4. Tendeur selon la revendication 1, dans lequel la partie de réception d'outil (92) décrit en outre un trou (93).
  5. Tendeur selon la revendication 1, dans lequel la partie de réception d'outil (92) s'étend radialement au-delà du mécanisme d'amortissement par rapport au pivot (34).
EP04776900A 2003-07-03 2004-06-22 Tensionneur reglable Expired - Lifetime EP1649193B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL04776900T PL1649193T3 (pl) 2003-07-03 2004-06-22 Napinacz regulowany

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/613,881 US7090606B2 (en) 2003-07-03 2003-07-03 Adjustable tensioner
PCT/US2004/019939 WO2005010402A1 (fr) 2003-07-03 2004-06-22 Tensionneur reglable

Publications (2)

Publication Number Publication Date
EP1649193A1 EP1649193A1 (fr) 2006-04-26
EP1649193B1 true EP1649193B1 (fr) 2009-02-11

Family

ID=33552788

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04776900A Expired - Lifetime EP1649193B1 (fr) 2003-07-03 2004-06-22 Tensionneur reglable

Country Status (16)

Country Link
US (1) US7090606B2 (fr)
EP (1) EP1649193B1 (fr)
JP (1) JP4384663B2 (fr)
KR (1) KR100784212B1 (fr)
CN (1) CN100458226C (fr)
AT (1) ATE422634T1 (fr)
AU (1) AU2004260046B2 (fr)
BR (1) BRPI0412098B1 (fr)
CA (1) CA2530822C (fr)
DE (1) DE602004019422D1 (fr)
ES (1) ES2318331T3 (fr)
MX (1) MXPA06000759A (fr)
PL (2) PL380267A1 (fr)
RU (1) RU2304733C2 (fr)
TW (1) TWI245859B (fr)
WO (1) WO2005010402A1 (fr)

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DE102004048284A1 (de) * 2004-10-05 2006-04-20 Ina-Schaeffler Kg Vorrichtung zum Befestigen und Spannen eines in einem Riementrieb einsetzbaren Aggregats
ITPI20040077A1 (it) * 2004-10-14 2005-01-14 Univ Pisa Meccanismo motoriduttore a rigidezza variabile e rapidamente controllabile
GB2419387A (en) * 2004-10-22 2006-04-26 Cnh Belgium Nv Belt tensioning mechanism
US7824286B2 (en) * 2005-03-28 2010-11-02 York Industries, Inc. Device for placing a looped belt under tension
DE102005056417A1 (de) * 2005-11-26 2007-05-31 Schaeffler Kg Spannvorrichtung zum Spannen eines Antriebsriemens beziehungsweise einer Antriebskette
EP2000703A1 (fr) * 2007-06-04 2008-12-10 Elbee Beheer BV Transmission continuellement variable et moyens de commande
WO2009035094A1 (fr) 2007-09-14 2009-03-19 Toppan Printing Co., Ltd. Feuille d'antenne, transpondeur et forme de livre
DE102008011074A1 (de) * 2008-02-26 2009-08-27 Schaeffler Kg Spanner für Zugmittel wie Riemen oder dergleichen
CN101886691A (zh) * 2010-06-29 2010-11-17 绵阳富临精工机械有限公司 具有新型锁止机构的棘爪式张紧装置
US8932163B2 (en) 2012-02-20 2015-01-13 Dayco Ip Holdings, Llc Belt tensioning device with variable spring factor
FR2987411B1 (fr) * 2012-02-27 2014-09-12 Skf Ab Dispositif tendeur d'un element de traction et procede de montage d'un tel dispositif
EP2951466B1 (fr) * 2013-01-30 2019-05-08 Cummins IP, Inc. Entretoise pour un tendeur de courroie
CN103171761B (zh) * 2013-04-12 2017-03-01 中航通飞研究院有限公司 一种防止飞机前轮摆振的装置
WO2014183200A1 (fr) * 2013-05-14 2014-11-20 Litens Automotive Partnership Tendeur avec amortissement amélioré
WO2015196304A1 (fr) * 2014-06-27 2015-12-30 Litens Automotive Partnership Agencement d'entraînement sans fin à poulie folle active
US9618099B2 (en) * 2015-07-13 2017-04-11 Gates Corporation Tensioner with secondary damping
US10066708B2 (en) * 2016-08-04 2018-09-04 Ford Global Technologies, Llc External spring to increase tension on belt tensioner for internal combustion engine
US20220099165A1 (en) * 2020-09-28 2022-03-31 Caterpillar Inc. Engine accessory drive system and one-piece bracket for same
CN114887700B (zh) * 2022-05-25 2023-11-21 上海华严环境科技有限公司 活性炭粉碎研磨装置

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Also Published As

Publication number Publication date
AU2004260046A1 (en) 2005-02-03
RU2006103069A (ru) 2006-06-10
TW200506245A (en) 2005-02-16
ES2318331T3 (es) 2009-05-01
CN1816705A (zh) 2006-08-09
RU2304733C2 (ru) 2007-08-20
KR20060038403A (ko) 2006-05-03
DE602004019422D1 (de) 2009-03-26
PL1649193T3 (pl) 2009-07-31
MXPA06000759A (es) 2006-04-18
CA2530822C (fr) 2008-09-02
AU2004260046B2 (en) 2008-01-24
JP2007516386A (ja) 2007-06-21
EP1649193A1 (fr) 2006-04-26
BRPI0412098B1 (pt) 2018-04-10
ATE422634T1 (de) 2009-02-15
JP4384663B2 (ja) 2009-12-16
PL380267A1 (pl) 2007-01-08
BRPI0412098A (pt) 2006-09-05
TWI245859B (en) 2005-12-21
KR100784212B1 (ko) 2007-12-11
WO2005010402A1 (fr) 2005-02-03
US7090606B2 (en) 2006-08-15
CN100458226C (zh) 2009-02-04
CA2530822A1 (fr) 2005-02-03
US20050003915A1 (en) 2005-01-06

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